EP0413317A1 - Auslassventilsteuervorrichtung für einen parallelen Mehrzylinder-Zweitaktmotor - Google Patents

Auslassventilsteuervorrichtung für einen parallelen Mehrzylinder-Zweitaktmotor Download PDF

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Publication number
EP0413317A1
EP0413317A1 EP90115603A EP90115603A EP0413317A1 EP 0413317 A1 EP0413317 A1 EP 0413317A1 EP 90115603 A EP90115603 A EP 90115603A EP 90115603 A EP90115603 A EP 90115603A EP 0413317 A1 EP0413317 A1 EP 0413317A1
Authority
EP
European Patent Office
Prior art keywords
exhaust
engine
cylinder
set forth
plane
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP90115603A
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English (en)
French (fr)
Other versions
EP0413317B1 (de
Inventor
Toshikazu Ozawa
Yu Motoyama
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Yamaha Motor Co Ltd
Original Assignee
Yamaha Motor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Yamaha Motor Co Ltd filed Critical Yamaha Motor Co Ltd
Publication of EP0413317A1 publication Critical patent/EP0413317A1/de
Application granted granted Critical
Publication of EP0413317B1 publication Critical patent/EP0413317B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/028—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation for two-stroke engines
    • F02D13/0284—Variable control of exhaust valves only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/36—Valve-gear or valve arrangements, e.g. lift-valve gear peculiar to machines or engines of specific type other than four-stroke cycle
    • F01L1/38—Valve-gear or valve arrangements, e.g. lift-valve gear peculiar to machines or engines of specific type other than four-stroke cycle for engines with other than four-stroke cycle, e.g. with two-stroke cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/10—Rotary or oscillatory slide valve-gear or valve arrangements with valves of other specific shape, e.g. spherical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
    • F02B25/26—Multi-cylinder engines other than those provided for in, or of interest apart from, groups F02B25/02 - F02B25/24
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/20—Shapes or constructions of valve members, not provided for in preceding subgroups of this group
    • F01L3/205—Reed valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B2075/1804—Number of cylinders
    • F02B2075/1812—Number of cylinders three
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • This invention relates to an exhaust control valve system for a parallel multi-cylinder, two-cycle engine and more particularly to an improved exhaust port and control valve arrangement for such an engine that permits a compact assembly.
  • port timing in two-cycle, crankcase compression, internal combustion engines is very critical to the engine performance. It is also known that port timings that permit maximum power attainment normally provide poor running at low and mid-ranges. In a like manner, port timings that provide good low and mid-speed range running do not permit maximum power output. It has, therefore, been proposed to employ an exhaust control valve in the exhaust port that is effective to change the exhaust timing and permit optimum engine performance through a wider range of running conditions.
  • This invention is adapted to be embodied in a multi-cylinder, two-cycle, crankcase compression, internal combustion engine having a cylinder block assembly that defines a pair of adjacent cylinder bores.
  • the cylinder bores have their axes lying in a common plane and a crankcase is positioned at one end of the cylinder bores.
  • Scavenge port means comprised of at least one scavenge passage extend from the crankcase to each of the cylinder bores.
  • An exhaust port extends from each of the cylinder bores for discharging exhaust gases from the respective cylinder to the atmosphere.
  • Exhaust control valve means is provided for varying the effective area and timing of operation of the exhaust ports.
  • the exhaust ports are disposed primarily within a quadrant defined by the plane and a plane perpendicular thereto and also extending through the respective cyinder bore axis.
  • the exhaust ports are formed at the end of exhaust passages that extend through the cylinder bore for discharging the exhaust gases to the atmosphere.
  • the exhaust passages have a central line that is disposed at an acute angle to the plane so that the exhaust passages are rotated relative to a plane extending through the cylinder bore axis and perpendicular to the first mentioned plane.
  • a two-cycle, crankcase compression, internal combustion engine constructed in accordance with this embodiment of the invention is identified generally by the reference numeral 11.
  • the engine 11 is of the three cylinder, in line type. It may be understood that the invention may be practiced in conjunction with engines having other numbers of cylinders and also with engines having V or opposed type configurations and two or more cylinders in each bank. It should be readily apparent to those skilled in the art how this invention can be practiced with such other engine configurations.
  • the engine 11 includes a cylinder block assembly 12 having three aligned cylinder bores 13 that are formed by pressed-in liners 14.
  • the cylinder bores 13 have their respective axes A, B and C lying in a common plane, indicated by the reference character D in Figure 1.
  • a crankcase member 15 is affixed, in a known manner, to the lower end of the cylinder block 12 at one end of the cylinder bores 13.
  • Pistons 16 are slidably supported within the cylinder bores 13 and are connected by means of connecting rods 17 to a crankshaft 18 that is journaled for rotation within individually sealed crankcase chambers 19 of the engine.
  • the crankcase chambers 19 are formed between the lower end of the cylinder block 12 and the crankcase member 15 and are each sealed relative to each other, as is conventional with two-cycle engine construction.
  • a cylinder head is affixed to the cylinder block 12 at the end opposite the crankcase member 15 and is formed with respective recesses 22 which cooperate with the cylinder bore 13 and pistons 16 to form the combustion chambers of the engine.
  • a charge forming system is provided for the engine and in accordance with the illustrated embodiments, this charge forming system includes an intake manifold 23 that is affixed to one side of the crankcase member 15 and which communicates with the chambers 19 through reed type check valve assemblies 24 which permits the flow of air into the crankcase chambers 19 but which prevents reverse flow when the piston 16 is compressing the air charge therein.
  • this charge forming system only pure air is inducted into the crankcase chambers 19. It is to be understood, however, that the invention can be utilized in conjunction with arrangements wherein a fuel/air charge is admitted to the crankcase chambers 19.
  • scavenge passages 25 may be considered to be a center scavenge while the passages 26 and 27 may be considered to be side scavenge passages.
  • the scavenge passages 25 would lie on planes E, F and G which are perpendicular to the plane D and which extend at right angles thereto and which intersect the cylinder bore axes A, B and C.
  • the side passages 26 and 27 would have their centers lying on the plane D.
  • this orientation would cause the engine to have a greater length than with the described embodiment to provide the necessary clearance for adjacent side scavenge passages.
  • these passages are rotated about the respective cylinder bore axes A, B and C so that the centers of the side scavenge passages 25 lie on planes H, I and J that are disposed at an acute angle to the planes E, F and G.
  • Each of the scavenge passages 25, 26 and 27 extends from the crankcase chambers 19 and enters the respective combustion chamber 22 through a respective scavenge port 28, 29 and 31.
  • the scavenge ports 28, 29 and 31 subtend an arc that is greater that 180 degrees of the cylinder bore 13.
  • the cylinder block 12 In confronting relationship to the scavenge passages 25, the cylinder block 12 is provided with exhaust passages 32 which extend from exhaust ports 33 that lie substantially within the quadrant defined by the planes D,E, D,F and D,G. The center of these passages 32 also lies along the planes H, I and J. This further adds in the compaction of the overall engine construction and affords good scavenging.
  • a fuel/air charge is admitted to each combustion chamber 22 by an air/fuel injector indicated generally by the reference numeral 34 and which has an air injector portion 35 that receives air under pressure from a suitable air compressor (not shown).
  • a fuel injection nozzle 36 injects fuel with the flow of fuel and air into the combustion chambers 22 being controlled by a suitable valve mechanism operated by a solenoid 37. Since the construction of the fuel/air injector 34 forms no part of the invention and since no other charge forming systems may be employed, further description of it is believed to be unnecessary.
  • the charge which is admitted to the chamber 22 is fired by a spark plug 38 in a known manner.
  • valves 39 are of a type that are affixed to respective valve shafts 41 that extend perpendicularly to the planes H, I and J at the upper end of the passages 32 and which have valve portions that are adapted to pass into a recess 40 formed between the cylinder liner 14 and the cylinder block 12 when the control valves 39 are positioned in their fully opened position as shown in Figure 3.
  • the exhaust port will open as soon as the pistons 16 move downwardly so as to uncover them and there will be a substantial overlap to achieve high power.
  • the control valves 39 are moved to the position shown in Figures 2 and 4 wherein they will partially obscure the exhaust ports 33 and cause a delay in their opening. This will improve significantly low speed running.
  • each control valve shaft 41 there is affixed to the exposed end of each control valve shaft 41 a respective pulley 42.
  • a respective wire actuator 43 is connected to each pulley 42 and is, in turn, connected at its other end to a respective pulley or groove 44 of a combined pulley that is affixed to the output shaft of a servo motor 45.
  • the servo motor 45 is controlled by an appropriate controlled strategy so as to control the timing in relation to engine speed and/or load or other characteristics so as to achieve the aforenoted results.
  • Figure 5 shows another arrangement for operating the exhaust control valves 39 all in unison. Because the basic construction of this embodiment is the same as the previously described embodiment, only the control valve actuating mechanism is illustrated since the basic porting arrangement is the same as that already described.
  • this embodiment also employs as actuators, pulleys 42, that are affixed to the control valve shafts 41 and which are associated with a servo motor 45. In this embodiment, however, a series chain of remote control wire actuators is interlinked between a pulley 101 that is affixed to the output shaft of the servo motor 45 and includes a first wire actuator 102 that extends from the pulley 101 to the pulley 42 of one of the control valve shafts 41.
  • a second wire actuator 103 extends from the other side of this first pulley 42 to the pulley 42 of the central throttle control valve shaft 41.
  • a third wire actuator 104 extends from the other side of this pulley 42 to the remaining pulley 42 of the remaining throttle control valve shaft 41.
  • This final pulley is then connected by means of a fourth wire actuator 105 back to the pulley 101 of the servo motor 45. As a result, operation of the pulley 101 will achieve simultaneous movement of all of the exhaust control valve shafts 41.
  • FIG 6 shows another embodiment of the invention which is basically the same as the embodiment of Figures 1 through 4 and differs from that embodiment and that of Figure 5 only in the manner in which the control valve shafts 41 are operated. Because of these similarities, the basic construction of the engine, the exhaust control valves and the exhaust control valve shafts 41 will not be described again. The description will be limited solely to the method and structure for operating the exhaust control valves 39 and exhaust control valve shafts 41.
  • the servo motor 45 couples an actuating shaft 151 that is rotatably journaled about an axis that lies parallel to the plane D and which is angularly disposed to the axes of rotation of the control valve shafts 41.
  • a plurality of lever arms 152 are formed either integrally with or affixed to the shaft 151 and have spherical pivotal connections 156 to links 153.
  • the opposite end of each of the links 153 is pivoted by means of a spherical pivotal connection 158 to a lever 154 that is affixed to the respective exhaust control valve shaft 41.
  • the shaft 151 and the exhaust valve shaft 41 are both mounted on the cylinder block. Consequently, the relationship of the positions between arm 152 and lever 154 may be very accurate.
  • the links, connecting the pivotable connections 156 to the pivotable connections 158 include adjustable screws. Therefore, the movement of each valve may be adjusted very accurately.
  • the exhaust control valves 39 have been flap type valves.
  • the invention can also be employed in connection with rotary type valves and Figures 7 and 8 show such an embodiment.
  • the basic construction of the engine 11 is the same as that previously described and, for that reason, components of this embodiment which are the same as the previously described embodiment have been identified by the same reference numerals and further description of components which are the same or substantially the same of the previously described embodiment are believed to be unnecessary.
  • the exhaust passages 32 are rotated from the planes E, F and G in a counterclockwise direction rather than the clockwise direction of the previously described embodiments.
  • the axes of the central portions of the exhaust passages 32 lie within the quadrant defined by the planes E, F and G and the plane D. Also, there is an acute angle between the planes as with the aforenoted embodiment but on the opposite side thereof.
  • control valves are rotatably journaled within the cylinder block 12 for controlling the effective opening of the exhaust ports 33 and the timing relationship thereof.
  • each control valve 201 has a cylindrical portion 202 that is disposed at one side of the ports 33 within the passages 32. Adjacent this cylindrical portion 202, the valves 201 are provided with a semicircular portion 203 which has a flat cutout edge 204 that actually forms a valving member with the port 33.
  • Each of the valves 201 further includes a control shaft portion 205 that is journaled within a closure plate 206 affixed to the side of the cylinder block.
  • a control disk or pulley 207 is affixed to the exposed end of each shaft 206 and may be operated in any of the aforedescribed manners. That is, the valves 201 may be operated all by individual flexible transmitters as in the embodiment of Figures 1 through 4, by a series train of flexible transmitters as the embodiment of Figure 5 or by a linkage system as with the embodiment of Figure 6.
  • the embodiments of the invention as described are all capable of providing good running under a wide variety of conditions through the control of the timing of the opening of the exhaust port and the area thereof. This can also be done with a very compact engine assembly due to the rotation of the exhaust ports from a plane perpendicular to the plane containing the axes of the cylinder bores.
  • the control valves are all supported for rotation about axes that extend generally perpendicularly to the exhaust passages.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
EP90115603A 1989-08-14 1990-08-14 Auslassventilsteuervorrichtung für einen parallelen Mehrzylinder-Zweitaktmotor Expired - Lifetime EP0413317B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP20791489 1989-08-14
JP207914/89 1989-08-14
JP166607/90 1990-06-27
JP2166607A JPH03156122A (ja) 1989-08-14 1990-06-27 並列多気筒２サイクルエンジンの排気制御弁装置

Publications (2)

Publication Number Publication Date
EP0413317A1 true EP0413317A1 (de) 1991-02-20
EP0413317B1 EP0413317B1 (de) 1997-03-05

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP90115603A Expired - Lifetime EP0413317B1 (de) 1989-08-14 1990-08-14 Auslassventilsteuervorrichtung für einen parallelen Mehrzylinder-Zweitaktmotor

Country Status (4)

Country Link
US (1) US5063888A (de)
EP (1) EP0413317B1 (de)
JP (1) JPH03156122A (de)
DE (1) DE69030035T2 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5337707A (en) * 1990-04-27 1994-08-16 Group Lotus Plc Internal combustion engine
EP0634570A2 (de) * 1993-06-14 1995-01-18 Yamaha Hatsudoki Kabushiki Kaisha Brennkraftmaschine mit Auslasssteuervorrichtung
US5783200A (en) * 1997-01-21 1998-07-21 The Procter & Gamble Company Personal cleansing compositions
US5785979A (en) * 1997-01-21 1998-07-28 The Procter & Gamble Company Personal cleansing compositions
EP1281844A2 (de) 2001-08-02 2003-02-05 AVL List GmbH Brennkraftmaschine

Families Citing this family (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3252196B2 (ja) * 1991-02-06 2002-01-28 ヤマハ発動機株式会社 筒内噴射２サイクルエンジン
SE468402B (sv) * 1991-07-01 1993-01-11 Dag Edlund Bladformade insugningsventiler till tvaataktsfoerbraenningsmotor
AT402323B (de) * 1992-01-16 1997-04-25 Avl Verbrennungskraft Messtech Zweitakt-brennkraftmaschine
JPH06193450A (ja) * 1992-12-25 1994-07-12 Yamaha Motor Co Ltd ２サイクルエンジンの排気制御弁装置
US5331927A (en) * 1993-10-07 1994-07-26 General Motors Corporation Exhaust port insert
JPH07224668A (ja) * 1994-02-07 1995-08-22 Sanshin Ind Co Ltd ２サイクルエンジンの可変圧縮機構
JPH07224669A (ja) * 1994-02-07 1995-08-22 Sanshin Ind Co Ltd Ｖ型多気筒２サイクルエンジン
IT1278827B1 (it) * 1995-04-28 1997-11-28 Monika Paszkowska Valvola termodinamica ad aspirazione
JP3586036B2 (ja) * 1996-04-18 2004-11-10 ヤマハ発動機株式会社 小型船舶用２サイクルエンジンの排気制御装置
JPH102225A (ja) * 1996-06-18 1998-01-06 Honda Motor Co Ltd 火花点火式２ストローク内燃機関の排気制御装置
JP3849813B2 (ja) * 1996-07-02 2006-11-22 本田技研工業株式会社 火花点火式２ストローク内燃機関の排気制御装置
JPH1054321A (ja) * 1996-08-08 1998-02-24 Toyota Motor Corp 燃料噴射ポンプのローラブッシュ
US6039012A (en) * 1996-09-18 2000-03-21 Yamaha Hatsudoki Kabushiki Kaisha Operating control system for 2 cycle direct injection engine
US6227922B1 (en) 1996-10-15 2001-05-08 Yamaha Hatsudoki Kabushiki Kaisha Exhaust timing control valve control arrangement
JP3597658B2 (ja) * 1996-12-25 2004-12-08 ヤマハ発動機株式会社 水上走行船用エンジン
JPH10238357A (ja) * 1997-02-24 1998-09-08 Yamaha Motor Co Ltd 小型船舶の排気構造
JP3836945B2 (ja) * 1997-05-23 2006-10-25 本田技研工業株式会社 ２サイクルエンジンの排気制御弁構造
US6158215A (en) * 1998-11-12 2000-12-12 Polaris Industries Inc. Varible exhaust resonance chamber valve system for two-cycle engines
US7367295B2 (en) * 2003-10-31 2008-05-06 Brp-Rotax Gmbh & Co. Kg Exhaust control valve for internal combustion engine
CA2495501A1 (en) * 2004-01-30 2005-07-30 Brp-Rotax Gmbh & Co., Kg. Exhaust-outlet control for 2-stroke engine
DE102004019021A1 (de) * 2004-04-20 2005-11-10 Bayerische Motoren Werke Ag Verfahren zum Betrieb einer 4-Takt-Brennkraftmaschine
JP2006199176A (ja) 2005-01-21 2006-08-03 Yamaha Motor Co Ltd スノーモービルの排気装置
JP2006199175A (ja) 2005-01-21 2006-08-03 Yamaha Motor Co Ltd スノーモービル
US8534261B2 (en) * 2007-05-09 2013-09-17 Hatamura Engine Research Office Ltd. Four-cycle engine
US8925502B1 (en) 2010-01-22 2015-01-06 Brp Us Inc. Hydraulically actuated valve assembly for an engine
EP3199787B1 (de) 2016-01-31 2019-02-13 BRP-Rotax GmbH & Co. KG Abgasventilanordnung für einen zweitakt-verbrennungsmotor

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1093764A (fr) * 1953-03-06 1955-05-09 Saurer Ag Adolph Dispositif de commande d'échappement pour moteurs à deux temps
US4121552A (en) * 1974-09-17 1978-10-24 Yamaha Hatsudoki Kabushiki Kaisha Exhaust means for two cycle engines
GB2175643A (en) * 1985-05-24 1986-12-03 Orbital Eng Pty Control of exhaust in ported two-stroke engines
WO1989004420A1 (en) * 1987-11-02 1989-05-18 Brunswick Corporation Improved exhaust valve throttling mechanism for two-stroke engine

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT369866B (de) * 1981-04-02 1983-02-10 Bombardier Rotax Gmbh Vorrichtung zur auslasszeitsteuerung von zweitakt -brennkraftmaschinen
SE465172B (sv) * 1985-05-24 1991-08-05 Orbital Eng Pty Foerfarande och anordning foer att reglera foeroreningsgraden i en foerbraenningsmotors avagaser
EP0212857B1 (de) * 1985-07-22 1990-01-17 Honda Giken Kogyo Kabushiki Kaisha Vorrichtung zur Steuerung der Auslasszeit einer Brennkraftmaschine
JPH0635832B2 (ja) * 1985-09-11 1994-05-11 本田技研工業株式会社 ２サイクルエンジンの排気時期制御装置
EP0246877A3 (de) * 1986-05-20 1989-02-01 Honda Giken Kogyo Kabushiki Kaisha Auslasssteuervorrichtung für Zweitaktbrennkraftmaschinen
JPH0826788B2 (ja) * 1987-03-02 1996-03-21 ヤマハ発動機株式会社 車輛の排気制御弁装置
JPS63255512A (ja) * 1987-04-13 1988-10-21 Honda Motor Co Ltd 多気筒２サイクルエンジン

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1093764A (fr) * 1953-03-06 1955-05-09 Saurer Ag Adolph Dispositif de commande d'échappement pour moteurs à deux temps
US4121552A (en) * 1974-09-17 1978-10-24 Yamaha Hatsudoki Kabushiki Kaisha Exhaust means for two cycle engines
GB2175643A (en) * 1985-05-24 1986-12-03 Orbital Eng Pty Control of exhaust in ported two-stroke engines
WO1989004420A1 (en) * 1987-11-02 1989-05-18 Brunswick Corporation Improved exhaust valve throttling mechanism for two-stroke engine

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5337707A (en) * 1990-04-27 1994-08-16 Group Lotus Plc Internal combustion engine
EP0634570A2 (de) * 1993-06-14 1995-01-18 Yamaha Hatsudoki Kabushiki Kaisha Brennkraftmaschine mit Auslasssteuervorrichtung
EP0634570A3 (de) * 1993-06-14 1995-06-28 Yamaha Motor Co Ltd Brennkraftmaschine mit Auslasssteuervorrichtung.
US5598813A (en) * 1993-06-14 1997-02-04 Yamaha Hatsudoki Kabushiki Kaisha Internal combustion engine with exhaust control device
US5783200A (en) * 1997-01-21 1998-07-21 The Procter & Gamble Company Personal cleansing compositions
US5785979A (en) * 1997-01-21 1998-07-28 The Procter & Gamble Company Personal cleansing compositions
EP1281844A2 (de) 2001-08-02 2003-02-05 AVL List GmbH Brennkraftmaschine
US6715455B2 (en) 2001-08-02 2004-04-06 Avl List Gmbh Internal combustion engine

Also Published As

Publication number Publication date
US5063888A (en) 1991-11-12
DE69030035T2 (de) 1997-06-12
EP0413317B1 (de) 1997-03-05
DE69030035D1 (de) 1997-04-10
JPH03156122A (ja) 1991-07-04

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